EP0035928A1 - Disc brake assembly - Google Patents

Disc brake assembly Download PDF

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Publication number
EP0035928A1
EP0035928A1 EP81400306A EP81400306A EP0035928A1 EP 0035928 A1 EP0035928 A1 EP 0035928A1 EP 81400306 A EP81400306 A EP 81400306A EP 81400306 A EP81400306 A EP 81400306A EP 0035928 A1 EP0035928 A1 EP 0035928A1
Authority
EP
European Patent Office
Prior art keywords
rotor
disc brake
pair
brake assembly
arm
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81400306A
Other languages
German (de)
French (fr)
Other versions
EP0035928B1 (en
Inventor
Irving R. Ritsema
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bendix Corp
Original Assignee
Bendix Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bendix Corp filed Critical Bendix Corp
Publication of EP0035928A1 publication Critical patent/EP0035928A1/en
Application granted granted Critical
Publication of EP0035928B1 publication Critical patent/EP0035928B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0008—Brake supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0041—Resilient elements interposed directly between the actuating member and the brake support, e.g. anti-rattle springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2200/00—Materials; Production methods therefor
    • F16D2200/0004—Materials; Production methods therefor metallic
    • F16D2200/0026—Non-ferro

Definitions

  • the present invention relates to a disc brake assembly wherein a rotor which is connected to a wheel assembly is engageable with a pair of friction elements to retard rotation of the rotor during braking.
  • a torque plate movably carries a caliper assembly which is operable to urge the pair of friction elements into engagement with the rotor.
  • the automobile In response to the energy crisis, the automobile is continually being downsized and redesigned to accept lighter materials to increase efficiency, as measured in miles per gallon.
  • the size of the disc or rotor must remain substantially large in diameter as the braking torque developed by the engagement of the friction elements with the rotor-is dependent on the diameter of the rotor at the location .of engagement.
  • Disc brake assemblies such as illustrated in United States Patents 3,442,353, 3,493,084 and 3,970,172 include steel caliper assemblies which are heavy and also spread out. Consequently, the efficiency or miles per gallon rating for automobiles with these disc brake assemblies are adversely affected by the latter.
  • the invention proposes a.disc brake assembly having a rotor to be braked, a torque plate fixedly disposed adjacent the rotor, a caliper assembly movably mounted on the torque plate and extending over a portion of the outer preiphery of the rotor, and a pair of friction elements disposed on opposite sides of the rotor and engageable therewith during braking to retard rotation of the rotor, the .
  • caliper assembly defining a central opening for receiving the torque plate characterized in that said caliper assembly defines an abutment surface forming a wall of the central opening, said abutment surface extending axially relative to the rotor to substantially overlap the pair of friction elements, said torque plate including an arm disposed outwardly of the radial dimension of the rotor and extending axially within the central opening to substantially overlap the rotor, said arm slidably engaging said abutment surface to absorb torque transmitted to said caliper assembly during braking, said torque plate also including a pair of projections disposed substantially within the radial dimension of the rotor and extending axially toward the rotor, said pair of projections being engageable with one of the pair of friction elements to absorb torque generated by the one friction element during braking.
  • the invention provides a disc brake assembly which accomodates a small clearance between the disc and a wheel.
  • the caliper assembly includes a hydraulic actuator and a bridge.
  • the bridge extends from the hydraulic actuator to a side of the rotor opposite the hydraulic actuator.
  • a pair of flanges defined by the bridge form arcuate segments substantially parallel with and adjacent an outer periphery of the rotor.
  • the bridge is made from a material which is different from the material of the hydraulic actuator and the material of the bridge defines a Brinell number less harder than for the hydraulic actuator.
  • the fridge is made. from aluminum while the hydraulic actuator and torque plate are made from steel.
  • the rotor diameter can be maintained sufficiently large to. generate braking torque during braking while the caliper assembly can be disposed within a small clearance between the rotor and a wheel assembly.
  • the torque plate cooperates with the caliper assembly to absorb braking torque at a horizontal location substantially in line with a center for the hydraulic actuator. Consequently, bending forces developed during braking by the caliper assembly are substantially offset and the lining area for a pair of friction elements can be increased.
  • Figure 1 is a front view of a disc brake assembly constructed in accordance with the present invention.
  • Figure 2 is a top view of the disc brake assembly of Figure 1.
  • Figure 3 is a cross-sectional view taken along line 3-3 of Figure 2.
  • a wheel assembly 10 which is associated with a vehicle, is coupled to a rotor or disc 12 so that the wheel and rotor move in unison:
  • a torque plate 14 is fixedly coupled to a non-rotatable portion of the vehicle and releasably supports a pair of pin assemblies -16 and 18.
  • a caliper assembly 20 slidably engaged the.pin assemblies to be movably mounted relative to the torque plate 14 and rotor 12.
  • the caliper assembly comprises a two-part assembly, one part being a hydraulic actuator 22 and a second part being a bridge 24.
  • a pair of friction elements 26 and 28 are disposed on opposite sides of the rotor so that upon operation of the hydraulic actuator 22, the friction element 26 is urged.directly into engagement with the rotor to develop'a reaction force' biasing the caliper .assembly to move to a position engaging the friction element 28 with the rotor.
  • Figure 2 shows the caliper assembly including a central opening 30 exposing the rotor.
  • the wall of the opening includes a pair of abutment surfaces 32 and 34 arcuately spaced from each other.
  • the pair-of abutment surfaces are formed on axially extending flanges 36 and 38 formed by the bridge part 24 of the caliper assembly.
  • the flanges 36 and 38 extend from separate inner legs 40 and 42 engaging the hydraulic actuator to a common outer leg 44 carrying the friction element 28 via suitable resilient means 46.
  • the legs 40 and 42 include grooves 48 and 50, respectively, for receiving ridges 52 and 54 formed on the hydraulic actuator 22.
  • the legs 40 and 42 are apertured to receive bolts 56 and 58 and the hydraulic actuator is provided with threaded bores at the ridges to releasably receive the bolts 56 and 58, thereby releasably coupling the bridge to the hydraulic actuator.
  • the torque plate 14 includes a first portion 60 which is parallel to the rotor 12 and provided with a cutout-62 for receiving a piston 64 of the hydraulic actuator 22.
  • a second portion 66 of the torque plate 14 extends axially from the first portion 60 into the . the central opening 30 to slidably engage the abutment surface 34.
  • the first portion slidably engages the abutment surface 34 and also the abutment surface 32.
  • the second portion includes a decreasing transverse width from the first portion to the rotor 12.
  • the torque plate 14 defines a pair of axially extending projections 68 and 70. The projections extend from the first portion 60 toward the rotor 12 to define abutment surfaces 72 and .74 which are engageable with the friction element 26 to absorb braking torque developed by the latter.
  • the bridge 24 is made from aluminum, while the hydraulic actuator can be made from a ferrous material, such as steel. or iron. Because braking torque developed by the friction element 28 is transmitted through the aluminum bridge 24, the flange portions 36 and 38 of the bridge 24 substantially overlaying the rotor 12 include an arcuate width A which is'larger than the largest arcuate width B for the arm 66. Consequently, the shear forces transmitted during braking to the aluminum bridge 24 are spread over a larger volume of material for the aluminum bridge than the steel arm.
  • Other materials are also possible in order to provide a lightweight construction for the disc brake assembly, for example, the torque plate, bridge and hydraulic actuator could be made from either magnesium or composite plastics.
  • An optional stop 76 is disposed between the flange 38, associated with the leading or forward portion of the bridge, and the arm 66.
  • the stop is secured to the flange 38, although it could also be secured to the arm 66, and includes top and bottom legs 78 and 80, see Figure 3, engageable with the arm 66.
  • the stop substantially eliminates radial movement between'the flange 38 and the arm 66.
  • the stop forms an abutment 79 which evenly.distributes braking forces along the flange 38.
  • the torque plate 14 could be an integral part of a knuckle in a vehicle and the two-part caliper assembly could be a single part. As such, these modifications and/or changes are included within the scope of the appended claims.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

A disc brake assembly includes a caliper assembly (20) which is movably mounted on a torque plate (14) to engage a pair of friction elements (26,28) with a rotor (12). The caliper assembly (20) defines a central opening (30) with abutment surfaces (32, 34) and one arm (66) of the torque plate extends into the central opening (30) to engage one (34) of the abutment surfaces (32.34).

Description

  • The present invention relates to a disc brake assembly wherein a rotor which is connected to a wheel assembly is engageable with a pair of friction elements to retard rotation of the rotor during braking. A torque plate movably carries a caliper assembly which is operable to urge the pair of friction elements into engagement with the rotor.
  • In response to the energy crisis, the automobile is continually being downsized and redesigned to accept lighter materials to increase efficiency, as measured in miles per gallon. However., the size of the disc or rotor must remain substantially large in diameter as the braking torque developed by the engagement of the friction elements with the rotor-is dependent on the diameter of the rotor at the location .of engagement. Disc brake assemblies such as illustrated in United States Patents 3,442,353, 3,493,084 and 3,970,172 include steel caliper assemblies which are heavy and also spread out. Consequently, the efficiency or miles per gallon rating for automobiles with these disc brake assemblies are adversely affected by the latter.
  • The invention proposes a.disc brake assembly having a rotor to be braked, a torque plate fixedly disposed adjacent the rotor, a caliper assembly movably mounted on the torque plate and extending over a portion of the outer preiphery of the rotor, and a pair of friction elements disposed on opposite sides of the rotor and engageable therewith during braking to retard rotation of the rotor, the . caliper assembly defining a central opening for receiving the torque plate characterized in that said caliper assembly defines an abutment surface forming a wall of the central opening, said abutment surface extending axially relative to the rotor to substantially overlap the pair of friction elements, said torque plate including an arm disposed outwardly of the radial dimension of the rotor and extending axially within the central opening to substantially overlap the rotor, said arm slidably engaging said abutment surface to absorb torque transmitted to said caliper assembly during braking, said torque plate also including a pair of projections disposed substantially within the radial dimension of the rotor and extending axially toward the rotor, said pair of projections being engageable with one of the pair of friction elements to absorb torque generated by the one friction element during braking.
  • The invention provides a disc brake assembly which accomodates a small clearance between the disc and a wheel. The caliper assembly includes a hydraulic actuator and a bridge. The bridge extends from the hydraulic actuator to a side of the rotor opposite the hydraulic actuator. A pair of flanges defined by the bridge form arcuate segments substantially parallel with and adjacent an outer periphery of the rotor.
  • In one-embodiment of the present invention,the bridge is made from a material which is different from the material of the hydraulic actuator and the material of the bridge defines a Brinell number less harder than for the hydraulic actuator. For example, the fridge is made. from aluminum while the hydraulic actuator and torque plate are made from steel.
  • It is an advantageous effect of the present invention that the rotor diameter can be maintained sufficiently large to. generate braking torque during braking while the caliper assembly can be disposed within a small clearance between the rotor and a wheel assembly. Also, the torque plate cooperates with the caliper assembly to absorb braking torque at a horizontal location substantially in line with a center for the hydraulic actuator. Consequently, bending forces developed during braking by the caliper assembly are substantially offset and the lining area for a pair of friction elements can be increased.
  • It is further advantageous effect of the present invention that a lightweight disc brake assembly results from the different materials utilized in the construction of the caliper assembly.
  • One way of carrying out the invention is illustrated in the drawings which are described in detail below.
  • Figure 1 is a front view of a disc brake assembly constructed in accordance with the present invention.
  • .Figure 2 is a top view of the disc brake assembly of Figure 1.
  • Figure 3 is a cross-sectional view taken along line 3-3 of Figure 2.
  • A wheel assembly 10, which is associated with a vehicle, is coupled to a rotor or disc 12 so that the wheel and rotor move in unison: A torque plate 14 is fixedly coupled to a non-rotatable portion of the vehicle and releasably supports a pair of pin assemblies -16 and 18. A caliper assembly 20 slidably engaged the.pin assemblies to be movably mounted relative to the torque plate 14 and rotor 12. The caliper assembly comprises a two-part assembly, one part being a hydraulic actuator 22 and a second part being a bridge 24. As is well known in the art, a pair of friction elements 26 and 28 are disposed on opposite sides of the rotor so that upon operation of the hydraulic actuator 22, the friction element 26 is urged.directly into engagement with the rotor to develop'a reaction force' biasing the caliper .assembly to move to a position engaging the friction element 28 with the rotor.
  • In accordance with the invention, Figure 2 shows the caliper assembly including a central opening 30 exposing the rotor. The wall of the opening includes a pair of abutment surfaces 32 and 34 arcuately spaced from each other. The pair-of abutment surfaces are formed on axially extending flanges 36 and 38 formed by the bridge part 24 of the caliper assembly. The flanges 36 and 38 extend from separate inner legs 40 and 42 engaging the hydraulic actuator to a common outer leg 44 carrying the friction element 28 via suitable resilient means 46. The legs 40 and 42 include grooves 48 and 50, respectively, for receiving ridges 52 and 54 formed on the hydraulic actuator 22. The legs 40 and 42 are apertured to receive bolts 56 and 58 and the hydraulic actuator is provided with threaded bores at the ridges to releasably receive the bolts 56 and 58, thereby releasably coupling the bridge to the hydraulic actuator.
  • The torque plate 14 includes a first portion 60 which is parallel to the rotor 12 and provided with a cutout-62 for receiving a piston 64 of the hydraulic actuator 22..A second portion 66 of the torque plate 14 extends axially from the first portion 60 into the . the central opening 30 to slidably engage the abutment surface 34. The first portion slidably engages the abutment surface 34 and also the abutment surface 32. The second portion includes a decreasing transverse width from the first portion to the rotor 12. In addition, the torque plate 14 defines a pair of axially extending projections 68 and 70. The projections extend from the first portion 60 toward the rotor 12 to define abutment surfaces 72 and .74 which are engageable with the friction element 26 to absorb braking torque developed by the latter.
  • In order to reduce weight the bridge 24 is made from aluminum, while the hydraulic actuator can be made from a ferrous material, such as steel. or iron. Because braking torque developed by the friction element 28 is transmitted through the aluminum bridge 24, the flange portions 36 and 38 of the bridge 24 substantially overlaying the rotor 12 include an arcuate width A which is'larger than the largest arcuate width B for the arm 66. Consequently, the shear forces transmitted during braking to the aluminum bridge 24 are spread over a larger volume of material for the aluminum bridge than the steel arm. Other materials are also possible in order to provide a lightweight construction for the disc brake assembly, for example, the torque plate, bridge and hydraulic actuator could be made from either magnesium or composite plastics.
  • An optional stop 76 is disposed between the flange 38, associated with the leading or forward portion of the bridge, and the arm 66. The stop is secured to the flange 38, although it could also be secured to the arm 66, and includes top and bottom legs 78 and 80, see Figure 3, engageable with the arm 66. The stop substantially eliminates radial movement between'the flange 38 and the arm 66. In addition, the stop forms an abutment 79 which evenly.distributes braking forces along the flange 38.
  • In figure 1, it is seen that the pair of projections 68 and 70 are located directly below the respective flanges 36 and 38. Moreover,. the flange 36 defines a center of mass at C and the flange 38 defines a center of mass at D. These centroids define a line CD which preferably intersects the center of the axis for the piston 64 of the hydraulic actuator 22 at E.
  • Numerous modifications and/or changes ot the aforegoing disc brake assembly are feasible by one skilled in the art. For example, the torque plate 14 could be an integral part of a knuckle in a vehicle and the two-part caliper assembly could be a single part. As such, these modifications and/or changes are included within the scope of the appended claims.

Claims (9)

1. A disc brake assembly having a rotor (12) to be braked, a torque plate (14) fixedly disposed adjacent the rotor, a caliper assembly (20) movably mounted on the torque plate (14) and extending over a portion of the outer periphery of the rotor (12), and a pair .of friction elements (26,28) disposed on opposite sides of the rotor (12), and engageable therewith during braking to retard rotation of the rotor, the caliper assembly (20) defining a central opening (30) for receiving the torque plate (14), characterized in that said caliper assembly (20) defines an abutment surface (34) forming a wall of the central opening (30), said abutment surface (34) extending axially relative to the rotor (12) to substantially overlap the pair of friction elements (26,28), said torque plate (14) including an arm (66) disposed outwardly-of the radial dimension of the rotor and extending axially within the central opening (30) to substantially overlap the rotor, said arm (66) slidably engaging said abutment (34) surface to absorb torque transmitted to said caliper assembly (20) during braking, said torque plate (14) also including a pair of projections (68,70) disposed substantially within the radial dimension of the rotor and extending axially toward the rotor, said pair of projections (68,70) being engageable with one (26) of the pair of friction elements to absorb torque generated by the one friction element (26) during-braking.
2. A disc brake assembly according to claim 1 characterized in.that the caliper assembly (20) comprises a two-part subassembly, one part (24) of said subassembly defining a bridge extending axially from one side of the rotor to the other side of the rotor and the other part (22) of said subassembly defining a hydraulic actuator, the one part (24) being made from a material which includes a Brinell number less harder than the Brinell number for the other part (22).
3. A disc brake assembly according to claim 2 characterized in that the two-part subassembly defines a pair of torque and groove connections (48-52, 50-54) extending substantially in a radial direction.
4. A disc brake assembly according to claim 2 characterized in that the one part (24) is made from aluminum and the other part (22) is made from a ferrous material.
5. A disc brake assembly according to any of the preceding claims characterized in that said arm (66) includes a decreasing transverse width from the one friction element (26) to the other friction element (28).
6. A disc brake assembly according to any of the preceding claims characterized in that said caliper assembly defines a radial width (A) outwardly of the outer periphery of the rotor and said arm (66) is substantially disposed within said. radial width (A).
7. A disc brake assembly according to any of the preceding claims characterized in that said torque plate (14) includes a first portion disposed within a plane substantially parallel to and adjacent one side of the rotor (12) and a second portion substantially perpendicular to said plane comprising said arm (66), said caliper assembly (20) including a second abutment surface (32) opposite said first mentioned abutment surface (34) and forming another wall of the central opening (30) and said first portion of said torque plate being engageable with a portion of said second abutment surface (32).
8. A disc brake assembly according to any of the preceding claims characterized in that said arm (66) and the caliper assembly (20) carry stop means (76) substantially preventing radial movement between the caliper assembly (20) and said arm (66).
9. A disc brake assembly according to claim 2 characterized in that said bridge (24) defines a pair of arcuately spaced flanges (36,38) having centroids (C,D) which define a line substantially intersecting the center (E) for the hydraulic actuator (22), said flanges (36,38) defining arcuate segments substantially parallel to and adjacent the outer periphery of the rotor.
EP81400306A 1980-03-06 1981-02-27 Disc brake assembly Expired EP0035928B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/127,708 US4345675A (en) 1980-03-06 1980-03-06 Disc brake assembly with lightweight and space saving characteristics
US127708 1980-03-06

Publications (2)

Publication Number Publication Date
EP0035928A1 true EP0035928A1 (en) 1981-09-16
EP0035928B1 EP0035928B1 (en) 1984-06-13

Family

ID=22431535

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81400306A Expired EP0035928B1 (en) 1980-03-06 1981-02-27 Disc brake assembly

Country Status (10)

Country Link
US (1) US4345675A (en)
EP (1) EP0035928B1 (en)
JP (1) JPS56134642A (en)
AR (1) AR222745A1 (en)
AU (1) AU533178B2 (en)
BR (1) BR8101375A (en)
CA (1) CA1155408A (en)
DE (1) DE3164051D1 (en)
ES (1) ES8207298A1 (en)
MX (1) MX154132A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2251466A (en) * 1990-12-11 1992-07-08 Nissin Kogyo Kk Disc brake
US5205383A (en) * 1990-12-11 1993-04-27 Nissin Kocyo Co., Ltd. Reaction force type disk brake

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JPS5712130A (en) * 1980-06-26 1982-01-22 Aisin Seiki Co Ltd Pin-slide type disc brake
US4548300A (en) * 1983-08-31 1985-10-22 Rockwell International Corporation Disc brake friction pad and stabilizing support
CH672982A5 (en) * 1987-06-18 1990-01-31 Steinemann Ag
JPH07745Y2 (en) * 1990-04-20 1995-01-11 日信工業株式会社 Reaction force type disc brake
US5620791A (en) * 1992-04-03 1997-04-15 Lanxide Technology Company, Lp Brake rotors and methods for making the same
DE19652123A1 (en) * 1996-12-14 1998-06-18 Teves Gmbh Alfred Brake calipers, in particular for motor vehicles
CN103557249B (en) * 2013-10-09 2016-04-13 贵州新安航空机械有限责任公司 A kind of device that can regulate brake block gap and brake block for convenience detach

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US3480116A (en) * 1965-05-06 1969-11-25 Girling Ltd Yoke mounting and guide means for spot-type disc brake
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US3552527A (en) * 1968-10-31 1971-01-05 Kelsey Hayes Co Disk brake caliper and mounting structure
GB1427245A (en) * 1973-07-24 1976-03-10 Girling Ltd Disc brakes
FR2232701B1 (en) * 1973-06-05 1977-02-04 Dba
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FR1180633A (en) * 1957-12-23 1959-06-08 Bendix Sa Disc brake improvements
FR76745E (en) * 1957-12-23 1961-11-24 Dba Sa Disc brake improvements
FR1227386A (en) * 1959-03-04 1960-08-19 Disc brake
FR78983E (en) * 1959-03-04 1962-10-05 Disc brake
FR1270684A (en) * 1960-07-22 1961-09-01 Dba Sa Sliding Case Disc Brake Improvements
US3480116A (en) * 1965-05-06 1969-11-25 Girling Ltd Yoke mounting and guide means for spot-type disc brake
DE1270341B (en) * 1966-02-09 1968-06-12 Bergische Stahlindustrie Partly lined disc brake
DE1914100A1 (en) * 1969-03-20 1970-10-01 Mueller Hermann E Fa Partly lined disc brake
US3651898A (en) * 1969-10-24 1972-03-28 Girling Ltd Disc brake caliper structure
DE2163586A1 (en) * 1970-12-22 1972-07-13 Girling Ltd Reaction type disc brake
FR2257819A1 (en) * 1974-01-11 1975-08-08 Dba Disc brake which is fitted on road vehicles - has pad support and cylinder assembly which slides laterally during braking
FR2346606A1 (en) * 1976-04-01 1977-10-28 Girling Ltd DISC BRAKE IMPROVEMENTS

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2251466A (en) * 1990-12-11 1992-07-08 Nissin Kogyo Kk Disc brake
US5205383A (en) * 1990-12-11 1993-04-27 Nissin Kocyo Co., Ltd. Reaction force type disk brake
GB2251466B (en) * 1990-12-11 1994-10-26 Nissin Kogyo Kk Disk brake

Also Published As

Publication number Publication date
US4345675A (en) 1982-08-24
AR222745A1 (en) 1981-06-15
CA1155408A (en) 1983-10-18
MX154132A (en) 1987-05-21
EP0035928B1 (en) 1984-06-13
ES500125A0 (en) 1982-09-01
AU533178B2 (en) 1983-11-03
ES8207298A1 (en) 1982-09-01
AU6740181A (en) 1981-09-10
JPS56134642A (en) 1981-10-21
BR8101375A (en) 1981-09-08
DE3164051D1 (en) 1984-07-19

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